EP2409014B1 - Pompe haute pression et module poussoir - Google Patents

Pompe haute pression et module poussoir Download PDF

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Publication number
EP2409014B1
EP2409014B1 EP10700440.0A EP10700440A EP2409014B1 EP 2409014 B1 EP2409014 B1 EP 2409014B1 EP 10700440 A EP10700440 A EP 10700440A EP 2409014 B1 EP2409014 B1 EP 2409014B1
Authority
EP
European Patent Office
Prior art keywords
pressure pump
pump
receptacle
roller shoe
centering guide
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP10700440.0A
Other languages
German (de)
English (en)
Other versions
EP2409014A1 (fr
Inventor
Gerhard Meier
Namik Karaosmanoglu
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Priority to PL10700440T priority Critical patent/PL2409014T3/pl
Publication of EP2409014A1 publication Critical patent/EP2409014A1/fr
Application granted granted Critical
Publication of EP2409014B1 publication Critical patent/EP2409014B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
    • F02M59/04—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by special arrangement of cylinders with respect to piston-driving shaft, e.g. arranged parallel to that shaft or swash-plate type pumps
    • F02M59/06—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by special arrangement of cylinders with respect to piston-driving shaft, e.g. arranged parallel to that shaft or swash-plate type pumps with cylinders arranged radially to driving shaft, e.g. in V or star arrangement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
    • F02M59/10—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
    • F02M59/10—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive
    • F02M59/102—Mechanical drive, e.g. tappets or cams
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F04B1/0408—Pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F04B1/0413—Cams
    • F04B1/0417—Cams consisting of two or more cylindrical elements, e.g. rollers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F04B1/0426—Arrangements for pressing the pistons against the actuated cam; Arrangements for connecting the pistons to the actuated cam
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/21—Elements
    • Y10T74/2101—Cams
    • Y10T74/2107—Follower

Definitions

  • the present invention relates to a high pressure pump for a fuel injection device of an internal combustion engine according to the preamble of claim 1 and a plunger assembly for a high pressure pump according to the preamble of claim 10.
  • High-pressure pumps for fuel injectors of internal combustion engines are known in the prior art, which have a plunger assembly with pressed into a plunger body roller shoe.
  • the plunger assembly is driven by a rotationally driven drive shaft of the high pressure pump, for example, against the force of a return spring in a lifting movement.
  • a high-pressure pump is described with at least one plunger assembly, which in turn has a hollow cylindrical plunger body and a roller shoe inserted therein in the direction of the longitudinal axis of the plunger body, in which a roller is rotatably mounted.
  • the high-pressure pump has at least one pump element, which in turn has a pump piston, by which a pump working space is limited.
  • the plunger assembly is disposed between the pump piston and a rotationally driven drive shaft of the high pressure pump, wherein the drive shaft has at least one cam or eccentric on which the roller runs.
  • the plunger body is guided displaceably in a bore of a housing part of the high-pressure pump.
  • the ram assembly serves to the rotational movement of the drive shaft in a To convert stroke movement of the pump piston.
  • the roller shoe is press-fitted into the ram body.
  • a high-pressure pump for a fuel injection device of an internal combustion engine, which has at least one pump element with a pump piston defining a pump chamber, wherein between the pump piston and a drive shaft of the high-pressure pump driven in rotation, a plunger assembly is provided with a plunger body and a pressed into a receptacle of the plunger body roller shoe wherein the plunger body has a centering guide for pressing the roller shoe.
  • the provision according to the invention of the centering guide enables an improved press-fitting of the roller shoe into the tappet body. A Schräginpressung is avoided, the centering an automatic centering is achieved, and thereby a robust ram assembly interference fit is created.
  • the centering guide is provided in the region of the receptacle.
  • the receptacle is cylindrical section-shaped, wherein the receptacle has an inner circumference, on which the centering guide is provided.
  • the centering guide on a chamfer is a chamfer.
  • the receptacle has a first end portion and a second end portion, wherein at the second end portion a radially projecting from the inner periphery inwardly abragender stop or projection is provided, and wherein the first end portion of an element of the drive shaft, in particular a cam or an eccentric , is opposite.
  • the centering guide is provided at the first end portion.
  • the centering guide is provided over a height of the first end portion in a range of 2 to 10 mm, in particular 4 mm.
  • the chamfer has a depth a in the range of 0.1 to 0.01 mm, in particular of 0.05 mm, and in an angle range of 30 to 60 °, in particular with an angle of 45 ° is trained.
  • a weakening of the plunger body by a centering guide with the above dimensions or in the above dimensional ranges has no adverse effects on the ram assembly interference fit. Neither the axial distance between the plunger body and the roller shoe is negatively affected in the plunger assembly during insertion or a pressure relief after pressing compared to a plunger assembly without centering, still affects a centering with the dimensions given above on the radial deformation of the plunger body during the pressing in and subsequent pressure relief negative. Rather, arises in terms of Plunger body with centering a more favorable deformation of the plunger body.
  • the roller shoe is formed with a cylindrical excess pressure, which in particular has a value P ü, nenn of 9 microns.
  • a plunger assembly for a high-pressure pump for a fuel injector of an internal combustion engine with a plunger body and a pressed into a receptacle of the plunger body roller shoe is also provided, wherein the plunger body has a centering for pressing in the roller shoe.
  • the plunger assembly is robust by providing the centering guide and has the advantages already described above.
  • a high-pressure pump 1 for a fuel injection device of an internal combustion engine is shown.
  • the high-pressure pump 1 has a housing 2, which is designed in several parts and in which a drive shaft 3 driven in rotation is arranged.
  • the drive shaft 3 is rotatably supported in the housing 2 via two spaced apart in the direction of the axis of rotation 4 of the drive shaft 3 bearings.
  • the bearings can be arranged in different housing parts 5, 6 of the housing 2.
  • the drive shaft 3 has at least one cam 7 or eccentric, wherein the cam 7 can also be designed as a multiple cam.
  • the high-pressure pump 1 has at least one or more arranged in each case 8 a housing part 8 pump elements 9, each with a pump piston 10 which is indirectly driven by the cam 7 of the drive shaft 3 in a lifting movement in at least approximately radial direction to the axis of rotation 4 of the drive shaft 3.
  • the pump piston 10 is guided in a cylinder bore 11 in the housing part 8 tightly displaceable and limited with its drive shaft 3 facing away from the end face in the cylinder bore 11 a pump working chamber 12th
  • the pump working space 12 has a connection with a fuel feed, for example a feed pump, via a fuel feed channel 13 extending in the housing 2.
  • a fuel feed for example a feed pump
  • a fuel feed channel 13 extending in the housing 2.
  • an opening into the pump chamber 12 inlet valve 14 is arranged, which has a spring-loaded valve member 15.
  • the pump working chamber 12 also has a connection extending in the housing part 8 fuel drain passage 16 to an outlet with an outlet, which is connected for example with a high-pressure accumulator 17.
  • With the high-pressure accumulator 17 one or more preferably arranged on the cylinders of the internal combustion engine injectors 18 are connected, is injected through the fuel in the cylinder of the internal combustion engine.
  • a from the pump working space 12th opening outlet valve 19 is arranged, which also has a spring-loaded valve member 20.
  • the pump element 9 is associated with a plunger assembly 21, via which the pump piston 10 is supported on the cam 7 of the drive shaft 3.
  • the plunger assembly 21 includes a hollow cylindrical plunger body 22 which is slidably guided in a bore 23 of a portion 5 of the housing 2 of the high-pressure pump 1.
  • the pump piston 10 has a smaller diameter than the plunger body 22 and protrudes with its pump chamber 12 facing away from the end of the cylinder bore 11 out and into the plunger body 22 into it.
  • the pump piston 10 may have a piston foot 24 which is enlarged in diameter relative to its remaining area.
  • the plunger assembly 21 and the pump piston 10 are pressed by a prestressed spring 27 to the cam 7 of the drive shaft 3 out.
  • the spring 27 is formed as the pump piston 10 surrounding and projecting into the plunger body 22 helical compression spring.
  • the spring 27 is supported on the one hand on the pump housing part 8 and on the other hand on a spring plate 28 from.
  • Fig. 2 shows an in Fig. 1 marked with II section of the plunger assembly 21 of the high-pressure pump 1 of Fig. 1 according to the prior art.
  • the spring plate 28 is connected to the pump piston 10 and is located on the side facing away from the roller shoe 26 of the annular web 29 at.
  • the spring 27 thus acts on the spring plate 28 both on the pump piston 10 and on the plunger body 22nd
  • a roller shoe 26 is inserted in the plunger body 22 of the drive shaft 3 side facing in the direction of the longitudinal axis 25 of the plunger body 22.
  • a cylindrical roller 31 is rotatably mounted in a cylinder-section-shaped receptacle 30 on the cam 7 of the drive shaft 3 facing side of the roller shoe 26.
  • the roller shoe 26 comes into abutment in the plunger body 22 in the direction of the longitudinal axis 25 against a stop 32 which is formed, for example, by a ring web projecting radially inwards from the plunger body 22.
  • FIGS. 3A, 3B, 3C each show a section of a plunger assembly 21 according to the prior art before, during and after the press-fitting process.
  • FIGS. 4A, 4B, 4C each show a section of a plunger assembly 21 according to an embodiment before, during and after the press-fitting process, wherein the receptacle 30 of the plunger body 22 is provided with a centering guide to be described later.
  • Fig. 3A shows an initial stage before the actual press-in process, in which a small force K is applied vertically from above or in the Y direction on the plunger body 22 to bring this into abutment with the roller shoe 26.
  • tappet body 22 is at a same in the Y direction on the plunger body 22 applied low force K of the roller shoe 26 already inserted into a first end portion 33 of the receptacle 30 of the plunger body 22.
  • a significantly higher pressing force or holding force is present between the plunger body 22 and the roller shoe 26 according to the embodiment than in the corresponding initial stage with respect to the plunger body 22 without centering and the roller shoe 26 according to the prior art.
  • Fig. 3B and Fig. 4B show a state during the actual press-fitting process, in which a significantly higher force K of 6 kN in the Y-direction is applied to the tappet body 22.
  • K a significantly higher force
  • the roller shoe 26 is inserted or pressed along an inner circumference 34 of the receptacle 30 of the plunger body 22 until the roller shoe 26 against the stop 32, which at a second end portion 35 of the receptacle 30 is provided, strikes.
  • Fig. 3C and 4C shown a state in which the roller shoe 26 has been pressed into the receptacle 30 of the plunger body 22 and no further force in the Y direction is exerted on the plunger body 22.
  • Fig. 5A again shows a detailed view of the in Fig. 3A illustrated initial stage, in which the plunger body 22 with the roller shoe 26 by low Force is brought into plant.
  • a distance d between the stop 32 at the second end portion 35 of the receptacle 30 and the first end portion 33 is 11.8 mm.
  • Fig. 5B is shown in the corresponding initial stage of the press-fitting operation of a roller shoe 26 in a provided with a centering tappet body 22 according to the embodiment (see Fig. 4A
  • the distance d has already been reduced to 7.8 mm, with the same force K being applied to the tappet body 22 as in FIG Fig. 5A shown installation state.
  • Fig. 6 shows a more detailed view of the in Fig. 5B illustrated installation state.
  • a centering guide 37 is formed on the inner periphery 34 over a height h of the receptacle 30 of 4 mm.
  • the provided on the inner circumference 34 centering guide has a chamfer a of 0.05 mm and an angle of 45 °, which allows the roller shoe 26, already introduced during the initial stage on the height h of the centering guide 37 in the receptacle 30 to be (see Fig. 4A . 5B ).
  • a robust plunger assembly 21 or a robust high-pressure pump 1 can be created. Due to the dimensions of the centering guide 37 causes no adverse weakening of the plunger body. Also, the behavior between the plunger body and the roller shoe with respect to the axial distance therebetween or with respect to the radial deformation of the plunger body in an initial stage, during Einpressvorgang itself or during the subsequent discharge is not adversely affected compared to a plunger body-roller shoe press assembly without centering according to the State of the art.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Fuel-Injection Apparatus (AREA)

Claims (10)

  1. Pompe haute pression (1) pour un dispositif d'injection de carburant d'un moteur à combustion interne, qui présente au moins un élément de pompe (9) avec un piston de pompe (10) limitant un espace de travail de pompe (12), un module de poussoir (21) avec un corps de poussoir (22) et un sabot à galet (26) pressé dans un logement (30) du corps de poussoir (22) étant prévu entre le piston de pompe (10) et un arbre d'entraînement (3) de la pompe haute pression (1) entraîné en rotation,
    caractérisée en ce que
    le corps de poussoir (22) présente un guide de centrage (37) pour presser le sabot à galet (26).
  2. Pompe haute pression (1) selon la revendication 1,
    caractérisée en ce que
    le guide de centrage (37) est prévu dans la région du logement (30).
  3. Pompe haute pression (1) selon la revendication 1 ou 2,
    caractérisée en ce que
    le logement (30) est réalisé sous forme de portion cylindrique, le logement (30) présentant une périphérie intérieure (34) sur laquelle est prévu le guide de centrage (37).
  4. Pompe haute pression (1) selon l'une quelconque ou plusieurs des revendications 1 à 3,
    caractérisée en ce que
    le guide de centrage (37) présente un biseau.
  5. Pompe haute pression (1) selon l'une quelconque ou plusieurs des revendications 1 à 4,
    caractérisée en ce que
    le logement (30) présente une première portion d'extrémité (33) et une deuxième portion d'extrémité (35), une butée (32) faisant saillie radialement vers l'intérieur depuis la périphérie intérieure (34) étant prévue sur la deuxième portion d'extrémité (35), et la première portion d'extrémité (33) étant opposée à un élément de l'arbre d'entraînement (3), en particulier une came (7) ou un excentrique.
  6. Pompe haute pression (1) selon la revendication 5,
    caractérisée en ce que
    le guide de centrage (37) est prévu sur la première portion d'extrémité (33).
  7. Pompe haute pression (1) selon la revendication 5 ou 6,
    caractérisée en ce que
    le guide de centrage (37) est prévu sur une hauteur h de la première portion d'extrémité (33) dans une plage de 2 à 10 mm, en particulier de 4 mm.
  8. Pompe haute pression (1) selon l'une quelconque ou plusieurs des revendications 4 à 7,
    caractérisée en ce que
    le biseau présente une profondeur a dans une plage de 0,1 à 0,01 mm, notamment une profondeur a de 0,05 mm, et est réalisé dans une plage angulaire de 30 à 60°, notamment avec un angle de 45°.
  9. Pompe haute pression (1) selon l'une quelconque ou plusieurs des revendications 1 à 8,
    caractérisée en ce que
    le sabot à galet (26) est réalisé avec un surdimensionnement de pressage cylindrique Pü,nenn, notamment avec un surdimensionnement de pressage cylindrique Pü,nenn de 9 µm.
  10. Module de poussoir (21) pour une pompe haute pression (1) pour un dispositif d'injection de carburant d'un moteur à combustion interne, comprenant un corps de poussoir (22) et un sabot à galet (26) pressé dans un logement (30) du corps de poussoir (22),
    caractérisé en ce que
    le corps de poussoir (22) présente un guide de centrage (37) pour presser le sabot à galet (26).
EP10700440.0A 2009-03-18 2010-01-20 Pompe haute pression et module poussoir Active EP2409014B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PL10700440T PL2409014T3 (pl) 2009-03-18 2010-01-20 Pompa wysokociśnieniowa i zespół popychacza

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102009001631A DE102009001631A1 (de) 2009-03-18 2009-03-18 Hochdruckpumpe und Stößelbaugruppe
PCT/EP2010/050612 WO2010105863A1 (fr) 2009-03-18 2010-01-20 Pompe haute pression et module poussoir

Publications (2)

Publication Number Publication Date
EP2409014A1 EP2409014A1 (fr) 2012-01-25
EP2409014B1 true EP2409014B1 (fr) 2013-05-01

Family

ID=42121024

Family Applications (1)

Application Number Title Priority Date Filing Date
EP10700440.0A Active EP2409014B1 (fr) 2009-03-18 2010-01-20 Pompe haute pression et module poussoir

Country Status (11)

Country Link
US (1) US20120080013A1 (fr)
EP (1) EP2409014B1 (fr)
JP (1) JP5497883B2 (fr)
KR (1) KR101673636B1 (fr)
CN (1) CN102356228B (fr)
BR (1) BRPI1013884B1 (fr)
DE (1) DE102009001631A1 (fr)
ES (1) ES2407864T3 (fr)
PL (1) PL2409014T3 (fr)
RU (1) RU2524476C2 (fr)
WO (1) WO2010105863A1 (fr)

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DE102011002814A1 (de) * 2011-01-18 2012-07-19 Robert Bosch Gmbh Rollenstößel
DE102011003678A1 (de) * 2011-02-07 2012-08-09 Robert Bosch Gmbh Hochdruckpumpe
JP5472340B2 (ja) * 2012-02-10 2014-04-16 株式会社デンソー 燃料供給ポンプ
DE102012211113A1 (de) * 2012-06-28 2014-01-02 Schaeffler Technologies AG & Co. KG Stößel
EP3173612B1 (fr) * 2015-11-24 2019-09-18 Aktiebolaget SKF Dispositif de galet à contre-came avec obturateur de retenue
WO2017181002A2 (fr) * 2016-04-15 2017-10-19 Koyo Bearings North America Llc Poussoir porvu d'une coupelle interne reçue sur une palette
DE102016219046A1 (de) * 2016-09-30 2018-04-05 Robert Bosch Gmbh Stößelbaugruppe für eine Radialkolbenpumpe, Radialkolbenpumpe
RU202059U1 (ru) * 2020-09-18 2021-01-28 Общество с ограниченной ответственностью Управляющая компания "Алтайский завод прецизионных изделий" Топливный насос высокого давления
RU207469U1 (ru) * 2021-07-19 2021-10-28 Общество с ограниченной ответственностью Управляющая компания "Алтайский завод прецизионных изделий" Толкатель топливного насоса высокого давления

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RU45479U1 (ru) * 2004-12-28 2005-05-10 Государственное образовательное учреждение высшего профессионального образования "Алтайский государственный технический университет им. И.И. Ползунова" (АлтГТУ) Кулачковый механизм привода плунжера топливного насоса высокого давления дизельного двигателя
DE102006041673A1 (de) * 2006-02-20 2007-08-23 Robert Bosch Gmbh Hochdruckpumpe, insbesondere für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine
CN201025197Y (zh) * 2007-04-23 2008-02-20 无锡威孚集团有限公司 一种用于高压共轨泵的强制润滑式滚子挺柱
CN101280753A (zh) * 2008-05-19 2008-10-08 宁波中策动力机电集团有限公司 一种柴油机喷油泵顶杆部件

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KR101673636B1 (ko) 2016-11-07
PL2409014T3 (pl) 2013-09-30
BRPI1013884B1 (pt) 2020-08-18
RU2524476C2 (ru) 2014-07-27
JP2012520423A (ja) 2012-09-06
JP5497883B2 (ja) 2014-05-21
US20120080013A1 (en) 2012-04-05
BRPI1013884A2 (pt) 2016-04-05
ES2407864T3 (es) 2013-06-14
WO2010105863A1 (fr) 2010-09-23
CN102356228A (zh) 2012-02-15
KR20110132567A (ko) 2011-12-08
CN102356228B (zh) 2014-07-09
DE102009001631A1 (de) 2010-09-23
EP2409014A1 (fr) 2012-01-25

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